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EP2245329B1 - Frein à disque - Google Patents

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Publication number
EP2245329B1
EP2245329B1 EP09704833.4A EP09704833A EP2245329B1 EP 2245329 B1 EP2245329 B1 EP 2245329B1 EP 09704833 A EP09704833 A EP 09704833A EP 2245329 B1 EP2245329 B1 EP 2245329B1
Authority
EP
European Patent Office
Prior art keywords
brake
sensor
calliper
disc
retaining bracket
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP09704833.4A
Other languages
German (de)
English (en)
Other versions
EP2245329A1 (fr
Inventor
Johann Baumgartner
Steffen Geissler
Stephan Pitzing
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH, Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP2245329A1 publication Critical patent/EP2245329A1/fr
Application granted granted Critical
Publication of EP2245329B1 publication Critical patent/EP2245329B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0977—Springs made from sheet metal
    • F16D65/0978—Springs made from sheet metal acting on one pad only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0008—Brake supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/007—Pins holding the braking members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/005—Force, torque, stress or strain

Definitions

  • the invention relates to a disc brake according to the preamble of claim 1.
  • Such disc brakes are operated position-controlled to achieve a stable control behavior.
  • the position of the brake actuator is determined by detecting the angular position of the drive motor, wherein the relationship between the rotational position and an achieved effect of the disc brakes is subject to large external influences. These include e.g. the state of wear, a temperature-dependent compressibility of the brake pads, the degree of clearance, so the distance between the brake pad and a brake disc in the unbraked position, as well as influences of a Schrägverschl devises the brake pads.
  • the invention has the object of further developing a disc brake of the generic type so that the determination of the clamping force with low design and manufacturing effort is possible and the operating costs of the disc brake can be lowered.
  • the invention makes use of the fact that an application-induced spreading of the caliper, which is known from analyzes of the deformation behavior of brake calipers for pneumatically actuated disc brakes, is proportional to the applied application force. In this case, this relationship is stable over the life of the caliper and is substantially subject, even with different operating conditions, only minor disturbances.
  • the invention is characterized in particular by the fact that it is extremely easy to implement and the required structural design basically requires only a few, easy to manufacture and to be assembled parts, which are also subject to only very low operational demands.
  • the low constructive and technical complexity arises mainly from the use of the disk brakes for commercial vehicles usually used retaining bracket as a correspondence to the sensor.
  • the relative movement of the saddle back to the saddle head counter to the application direction is determined by a change in position of the saddle head or saddle rigidly mounted retaining bracket to the opposite fixed to the brake caliper sensor and transmitted to an evaluation unit.
  • the installation of only one sensor is sufficient, which can be arranged on the outside of the brake caliper and can be arranged unaffected by the forces acting on an application device.
  • a temperature dependence of the measurement signal can be sufficiently reduced by appropriate measures.
  • the resulting change in the distance between the saddle back and the saddle head and the size to be measured resulting from a braking-induced heating of the caliper is compensated for by the component corresponding to the sensor, fixed on one side by a corresponding structural design, an adapted choice of material and a corresponding arrangement on the caliper of the same thermal expansion is subject, as the caliper itself or its tension struts.
  • a compensation possibly resulting error due to different thermal expansion can be done by an automatic initialization of the evaluation at predetermined time intervals between the measuring operations and possibly a correction calculation, which is based on an evaluation of the energy converted by the brake.
  • This initialization can be done by that in the non-actuated position of the brake e.g. at intervals of minutes, the distance signal between the fixed component and the sensor is detected.
  • the determination of the Zuspannweges the brake on the engine position signal includes in addition to the saddle spread, the clearance of the brake as well as a caused by compressibility and unevenness of the brake pads compression stroke.
  • the senor is formed in correspondence with the base element forming headband or with a separate base element attached thereto as a Hall sensor, wherein the fixed relative to the headband Hall sensor is energized, while the headband is designed as a magnet or carries a magnet that moves past the Hall sensor.
  • This method allows a correspondingly large linear measuring range, compared to one in which the headband is moved towards the sensor.
  • the correspondence part on the caliper and the sensor may be attached to the headband.
  • a maximum possible amount of the relative displacement of the retaining clip to the Hall sensor of 1, 5 mm, a linear measuring range of the Hall sensor of 4.5 mm is applied.
  • scattering of the absolute value for example due to tolerance influences or thermal expansion, in the range of 3 mm, ie twice the amount of the maximum possible measured value, can be compensated.
  • the single FIGURE shows a disc brake in a perspective view.
  • a pneumatically or electromechanically operable disc brake which has a brake caliper 1, which engages over a brake disc 5 and in the both sides of the brake disc 5 arranged brake pads 6 are mounted, which can be pressed by means of an application device for braking against the brake disc 5.
  • the caliper consists of a saddle head 2 and a saddle back 3, which are interconnected by two tie rods 4, which extend in the axial direction of the brake disc 5 and the circumferential direction of the brake disc 5 define a mounting opening 14 of the caliper 1.
  • the brake pads 6 are held under preload in the brake caliper 1, to which each brake pad 6 has a pad retaining spring 7, on which a headband 8 is supported.
  • the retaining clip 8 spans the assembly opening 14 and extends in its length in the axial direction of the brake disk 5.
  • the holding bracket 8 In its end portion facing the receiving pocket 10, the holding bracket 8 has a U-shaped measuring bracket 11, whose two legs each have a sensor 12 fixedly connected to the saddle head 2, the contactless contact in the region of a measuring point 13 in operative connection with the associated leg of the measuring bracket 11 is in operative connection.
  • These sensors 12 are connected to an evaluation unit, not shown, for determining the effective brake application force.
  • This dimensional change is effective by an enlargement of a gap between the respective leg of the measuring bracket 11 and the associated sensor 12 at the measuring point 13 and detected by the sensor 12.
  • the measuring bracket 11 and the sensor 12 shown in the exemplary embodiment in the application direction this is, if it is designed as a Hall sensor, arranged next to the headband 8 and the measuring bracket 11, wherein the headband 8 as a correspondence element with a rod-shaped permanent magnet, for example can be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Claims (9)

  1. Frein à disque ayant un étrier (1) de frein recouvrant un disque (5) de frein et ayant une tête (2) d'étrier et un arrière (3) d'étrier qui y est relié par des tirants (4) et dans lequel sont montées des garnitures (6) de frein, pouvant être pressées des deux côtés sur le disque (5) de frein et fixées radialement, au moyen d'un arceau (8) de maintien s'étendant dans la direction axiale du disque (5) de frein, et comprenant un dispositif de mesure raccordé à une unité d'exploitation et destiné à déterminer la force de serrage appliquée lors du freinage, caractérisé en ce que le dispositif de mesure a deux éléments de base, mobiles l'un par rapport à l'autre dans la direction de serrage, dont l'un est constitué en capteur (12) et dont l'autre est constitué sous la forme d'une partie correspondante en liaison active avec lui, un élément de base étant disposé sur l'arceau (8) de maintien, serré d'un côté sur la tête (2) de l'étrier ou sur l'arrière (3) de l'étrier et l'autre élément de base étant monté sur l'étrier (1) de frein, du côté opposé au côté de serrage de l'arceau (8) de maintien.
  2. Frein à disque suivant la revendication 1, caractérisé en ce que l'arceau (8) de maintien est fixé à l'arrière (3) de l'étrier et le capteur (12) à la tête (2) de l'étrier, l'arceau (8) de maintien étant monté coulissant dans une poche (10) de réception de la tête (2) de l'étrier.
  3. Frein à disque suivant l'une des revendications 1 ou 2, caractérisé en ce que l'arceau (8) de maintien a, dans sa partie d'extrémité libre éloignée de l'arrière de l'étrier, comme partie de correspondance, un arceau (11) de mesure qui correspond au capteur (12).
  4. Frein à disque suivant l'une des revendications 1 à 3, caractérisé en ce que l'arceau (11) de mesure est en forme de U, chaque branche de l'arceau (11) de mesure étant associée à un capteur (12).
  5. Frein à disque suivant l'une des revendications 1 à 4, caractérisé en ce que le capteur (12) est un capteur sans contact.
  6. Frein à disque suivant l'une des revendications 1 à 5, caractérisé en ce que la dilation longitudinale due à la chaleur du barreau de mesure ou de l'arceau (8) de maintien correspond, pour une même charge calorifique, à la dilatation longitudinale des tirants (4).
  7. Frein à disque suivant l'une des revendications 1 à 6, caractérisé en ce que le capteur (12) est constitué sous la forme d'un capteur de Hall.
  8. Frein à disque suivant l'une des revendications 1 à 7, caractérisé en ce que l'arceau (8) de maintien a un aimant permanent, de préférence sous forme de barreau, qui correspond au capteur de Hall.
  9. Frein à disque suivant l'une des revendications 1 à 8, caractérisé en ce que le capteur de Hall est disposé, dans la direction de serrage, à côté de l'arceau (8) de maintien.
EP09704833.4A 2008-01-22 2009-01-13 Frein à disque Active EP2245329B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008005430 2008-01-22
PCT/EP2009/000134 WO2009092525A1 (fr) 2008-01-22 2009-01-13 Frein à disque

Publications (2)

Publication Number Publication Date
EP2245329A1 EP2245329A1 (fr) 2010-11-03
EP2245329B1 true EP2245329B1 (fr) 2014-03-19

Family

ID=40568292

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09704833.4A Active EP2245329B1 (fr) 2008-01-22 2009-01-13 Frein à disque

Country Status (5)

Country Link
US (1) US8627929B2 (fr)
EP (1) EP2245329B1 (fr)
DE (1) DE102009004424A1 (fr)
ES (1) ES2461118T3 (fr)
WO (1) WO2009092525A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009041951B4 (de) * 2009-09-17 2020-04-02 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Messanordnung zur Zuspannkraftmessung einer Scheibenbremse und eine entsprechende Scheibenbremse
DE102010043320A1 (de) * 2010-11-03 2012-05-03 Continental Teves Ag & Co. Ohg Vorrichtung und Verfahren zur Ermittlung einer Maßgröße für eine wirkende Bremskraft oder Reibkraft an einer Scheibenbremse
DE102012007471B4 (de) 2012-04-13 2014-12-18 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Messanordnung zur Zuspannkraftmessung einer Scheibenbremse und eine entsprechende Scheibenbremse
DE102012016712A1 (de) * 2012-08-22 2014-02-27 Wabco Radbremsen Gmbh Scheibenbremse, insbesondere für Nutzfahrzeuge, sowie Bremssattel für eine solche Scheibenbremse
DE102012016735B4 (de) * 2012-08-22 2017-11-23 Wabco Radbremsen Gmbh Scheibenbremse, insbesondere für Nutzfahrzeuge
DE102012108667A1 (de) * 2012-09-17 2014-03-20 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Anordnung eines Belaghaltebügels am Bremssattel einer Scheibenbremse sowie Bremsbelag
DE102013008155A1 (de) * 2013-05-13 2014-11-13 Wabco Europe Bvba Sattelscheibenbremse eines Fahrzeugs, insbesondere eines Nutzfahrzeugs, und Niederhalteeinrichtung einer solchen Bremse
DE102013008161A1 (de) * 2013-05-13 2014-11-13 Wabco Europe Bvba Sattelscheibenbremse eines Fahrzeugs, insbesondere eines Nutzfahrzeuges, und Bremssattel einer solchen Bremse
DE102014115764A1 (de) * 2014-10-30 2016-05-04 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Aus Gusseisen bestehender Bremssattel einer Scheibenbremse
DE102014019619A1 (de) * 2014-12-29 2016-06-30 Wabco Europe Bvba Scheibenbremse, insbesondere für Nutzfahrzeuge
US10113599B2 (en) 2017-02-07 2018-10-30 Edwin Beachy Retaining bracket for disc brake caliper and kit including the same
US10718829B2 (en) * 2018-10-26 2020-07-21 Sensata Technologies, Inc. Optimizing utilization of a wireless position sensor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19849309B4 (de) * 1998-10-26 2010-09-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse für ein Nutzfahrzeug
SE523555C2 (sv) * 2001-09-07 2004-04-27 Haldex Brake Prod Ab Modulformad skrivbroms för ett fordon
DE10148472A1 (de) 2001-10-01 2003-04-17 Knorr Bremse Systeme Scheibenbremse und Verfahren zur Bestimmung der Bremskraft einer Scheibenbremse
EP1748213A1 (fr) 2005-07-25 2007-01-31 Siemens Aktiengesellschaft Frein à disque avec dispositif amélioré pour mesurer la force normale
DE102006029978B3 (de) * 2006-06-29 2007-11-08 Siemens Ag Verfahren und eine Vorrichtung zum Messen einer wirkenden Normalkraft an einer Scheibenbremse
US20080257657A1 (en) * 2007-04-17 2008-10-23 Bendix Spicer Foundation Brake Llc Wrong Wheel Warning Sensor

Also Published As

Publication number Publication date
ES2461118T3 (es) 2014-05-16
DE102009004424A1 (de) 2009-07-30
EP2245329A1 (fr) 2010-11-03
WO2009092525A1 (fr) 2009-07-30
US20110005872A1 (en) 2011-01-13
US8627929B2 (en) 2014-01-14

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